JP4562368B2 - Rotation actuated one-way clutch - Google Patents

Description

  The present invention relates to a rotationally actuated one-way clutch that is used in motorcycles, snowmobiles, and the like and that exhibits the function of a one-way clutch when a predetermined rotational speed is exceeded.

  Generally, a one-way clutch has an outer ring and an inner ring that rotate relative to each other, and sprags and rollers that transmit torque between the outer ring and the inner ring mesh with a cam surface provided on a raceway surface of the outer ring or the inner ring, thereby Only the rotational torque is transmitted. In addition, it is configured to idle in the reverse direction.

  In such a one-way clutch, a roller is disposed in a pocket (recess) provided in the inner ring or outer ring, and the rotation is locked by a wedge action in which the roller engages a wedge portion of the pocket depending on the rotation direction. What is known.

  For example, in Patent Document 1, when a roller is disposed in a recess provided in an outer ring (outer race) and the outer ring rotates clockwise, the roller is locked in the recess by a wedge action, and the outer ring is A configuration for locking the rotation is disclosed.

  Further, in Patent Document 2, a roller and an auxiliary roller are arranged between an outer ring (outer race) and an input coupling, and when the rotational speed exceeds a predetermined number, the auxiliary roller presses the roller with centrifugal force. With this pressing force, when rotating in a predetermined direction, the roller can be locked by a wedge action, and a configuration that exhibits the function of a one-way clutch is disclosed.

Prior art document information related to the invention of this application includes the following.
Japanese Examined Patent Publication No. 53-8019 (page 1-2, Fig. 1 etc.) Japanese Patent Laid-Open No. 52-100045 (page 2-3, FIG. 3, etc.)

  The one disclosed in Patent Document 1 is a general one-way clutch using a roller, and is not configured to lock according to the number of rotations.

  Patent Document 2 discloses a configuration that locks according to the number of rotations. However, since the long hole for determining the operating range of the auxiliary roller is provided separately from the outer ring, it is difficult to obtain the desired dimensional accuracy of the apparatus, and the number of parts increases. Further, there is a possibility that the auxiliary roller may be caught in the long hole, and parts such as a plate and a holding piece for pressing the roller are required, and a space for installing the spring is required, so that the diameter of the apparatus is limited.

  In addition, a coil spring is provided in the spring that biases the roller. However, it is difficult to set a small spring constant in a limited space with a coil spring, which is expensive in comparison with an accordion spring or the like. There is a risk of becoming.

  Therefore, the present invention reduces the number of parts, is inexpensive, can set a small spring constant, easily obtains dimensional accuracy, does not cause a weight to be caught, and has a structure that can be designed even in a space-saving manner. The purpose is to provide.

In order to achieve the above object, the rotationally actuated one-way clutch of the present invention comprises:
An outer ring having an inner peripheral cylindrical surface, an inner ring formed with a cam surface, a rolling element that transmits torque between the outer and inner rings, a biasing spring that biases the rolling element, and a biasing force that receives centrifugal force A rotary operation type one-way clutch provided with a weight body that presses the rolling element in an engagement direction while resisting the urging force of a spring, and is provided with a locking portion that limits an operation range of the weight body. It is said.

In order to achieve the above object, the rotationally operated one-way clutch of the present invention is
An outer ring having an inner peripheral cylindrical surface, an inner ring formed with a cam surface, a rolling element that transmits torque between the outer and inner rings, a biasing spring that biases the rolling element, and a biasing force that receives centrifugal force A retainer for holding at least one of the rolling element, the weight body, and the urging spring in a rotationally actuated one-way clutch provided with a weight body that presses the rolling element in the engaging direction while resisting the urging force of the spring. The cage is provided with a bearing portion that supports the space between the outer and inner rings.

In order to achieve the above object, the rotationally operated one-way clutch of the present invention is
An outer ring having an inner peripheral cylindrical surface, an inner ring formed with a cam surface, a rolling element that transmits torque between the outer and inner rings, a biasing spring that biases the rolling element, and a biasing force that receives centrifugal force A retainer that holds at least one of the rolling element, the weight body, and the urging spring in a rotationally actuated one-way clutch provided with a weight body that presses the rolling element in the engaging direction while resisting the urging force of the spring. And a detent mechanism that prevents relative rotation between the cage and the inner ring.

In order to achieve the above object, the rotationally operated one-way clutch of the present invention is
An outer ring having an inner peripheral cylindrical surface, an inner ring formed with a cam surface, a rolling element that transmits torque between the outer and inner rings, a biasing spring that biases the rolling element, and a biasing force that receives centrifugal force In a rotationally actuated one-way clutch provided with a weight that presses the rolling element in the engaging direction while resisting the biasing force of the spring, the resin-made holding at least one of the rolling element, the weight, and the biasing spring The cage is provided.

According to the present invention, the following effects can be obtained.
The urging spring urges the rolling element in the direction of non-engagement with the cam surface, and the pocket receives the centrifugal force and resists the urging force of the urging spring to engage the rolling element with the cam surface. Since the weight that pushes in the direction is arranged, the number of parts can be reduced, the spring constant can be set small, inexpensively, dimensional accuracy can be easily obtained, there is no risk of the weight getting caught, and space-saving design is possible. A rotationally actuated one-way clutch having a structure can be provided.

Further, the specific effects obtained for each claim are as follows.
According to the configurations of claims 1 and 6, it is possible to prevent a malfunction in which the weight body jumps out to the cam surface side immediately after receiving the excessive torque and does not return to the weight operation surface side.
According to the configuration of the second, third, seventh and eighth aspects, the inner and outer rings can be kept concentric without using separate bearing parts or the like.
According to the configuration of the fourth, ninth and twelfth aspects, it is possible to prevent positioning of the cage and displacement in the circumferential direction.
According to the structure of Claim 5 and 10, since frictional resistance with a weight body is comparatively few, an operation | movement becomes smooth. In addition, the entire apparatus can be lightened.
According to the structure of claim 11, the operation of the weight body is smooth.
According to the configuration of the thirteenth aspect, it is possible to easily check the missing part of the weight body.

  In this specification, “rotation operation type” means that the function as a one-way clutch operates reliably during rotation in a range exceeding the predetermined rotation speed. Even if the rotation is less than the number of rotations, it may function as a one-way clutch. The “predetermined number of rotations” is arbitrarily determined by the mass of the weight, the distance from the center of the inner ring of the weight, and the inclination angle of the weight operating surface.

  Further, in this specification, the “weight operating surface” is a surface that is guided by rolling or sliding a weight body that has received centrifugal force to the outer diameter side along this surface, and is in contact with the roller. The roller is provided to move the roller to the meshing position. The “weight operation surface” is preferably inclined so that the circumferential width of the pocket gradually decreases in the outer diameter direction.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. In the drawings, the same parts are denoted by the same reference numerals.

  A first embodiment of the present invention will be described. FIG. 1 is a front view of a rotary actuated one-way clutch 30 showing a first embodiment, and FIG. 2 is a schematic view of a pocket portion viewed from the outer diameter side of the first embodiment. The rotationally actuated one-way clutch 30 has a spline 2a engraved on the inner periphery, and is coaxial with the inner ring 2 that is a hollow shaft fitted to a drive shaft (not shown), radially outside the inner ring 2, and the inner ring 2 and an outer ring 3 arranged to be relatively rotatable.

  In the first embodiment, a pocket that accommodates a roller, a weight body, an accordion spring, and the like constituting the one-way clutch portion is constituted by the outer peripheral surface of the inner ring 2 and the window portion 43 provided in the cage 32.

  The substantially annular retainer 32 disposed between the outer ring 3 and the inner ring 2 is a retainer body, and a substantially annular support plate 34 is provided on an end surface in the axial direction of the retainer 32. The support plate 34 is fixed to the cage 32 by the cage coupling portion 33.

  As shown in FIGS. 1, 2, and 4, on the outer ring 3 side of the cage 32, a bearing portion 20 that is slidable on the inner peripheral surface 3 a (see FIGS. 9 to 11) of the outer ring 3 is provided. Yes. The bearing portion 20 has a function of supporting the inner ring 2 and the outer ring 3 concentrically. Further, the bearing portion 20 having a predetermined length in the circumferential direction is provided between the window portions 43 so as to be equally divided in the circumferential direction.

  An accordion spring 35 that urges the roller 37 from a substantially tangential direction, a roller 37 that transmits torque between the outer ring 3 and the inner ring 2, and a roller 37 A weight 38 that acts on the roller 37 to press the roller 37 in the meshing direction is disposed. When the weight body 38 is not acting, a part of the weight body 38 is accommodated in the recess 31 provided on the outer peripheral surface of the inner ring 2. The inner peripheral edge of the support plate 34 is located on the outer diameter side from the recess 31, and the communication portion 6 is formed so that a part of the weight body 38 can be seen. With this communication portion 6, after the assembly of the device (rotation actuated one-way clutch), the presence or absence of the weight body 38 can be easily confirmed by visual recognition, and the missing item can be easily confirmed.

  The retainer 32 is provided with a concave portion 36 having a substantially U-shaped radial cross section, and an end portion of the accordion spring 35 opposite to an end portion that applies a biasing force to the roller 37 is fitted into the concave portion 36 (see FIG. 4). Are held together.

  As can be seen from FIG. 2, the window portion 43 of the cage 32 is formed through the cage 32 in the axial direction, leaving a wall portion. The open end in the axial direction of the window portion 43 is closed by the support plate 34 described above. Accordingly, the accordion spring 35, the roller 37, and the weight body 38 accommodated in the window 43 are held in the axial direction by the wall of the cage 32 and the support plate 34, and are held in the radial direction by the outer ring 3 and the inner ring 2. And does not deviate from the window 43.

  FIG. 3 is an axial sectional view of the rotary actuated one-way clutch 30. It can be seen that the support plate 34 is fixed to the cage 32 by the cage coupling portion 33. It can also be seen that the roller 37 has a small clearance between the wall of the cage 32 and the support plate 34 and is supported in the axial direction.

  Next, the operation of the rotationally actuated one-way clutch 30 of the first embodiment will be described with reference to FIGS. FIG. 4 is a diagram showing a state of the roller and the weight body during non-rotation to low-speed rotation in the first embodiment, and FIG. 5 is a view of the roller and weight body during operation (when meshing) of the first embodiment. FIG. 6 is a diagram showing the state of the roller and the weight body when the eccentricity is in the first embodiment (when over-torque is received).

  Here, the configuration of the first embodiment will be described in more detail with reference to FIG. The cage 32 includes a plurality of convex portions 44 that fit into a plurality of concave grooves 45 provided on the outer circumferential surface of the inner ring 2 equally in the circumferential direction. Since the convex portion 44 is fitted in the concave groove 45, the cage 32 and the inner ring 2 are configured not to rotate relative to each other. That is, the concave groove 45 and the convex portion 44 constitute a rotation prevention mechanism that prevents relative rotation between the cage 32 and the inner ring 2.

  A weight operating surface 40 is formed on one side surface of the window portion 43 of the cage 32, and when the weight body 38 receives centrifugal force, the weight body 38 moves to the outer diameter side along this surface and is pressed against the roller 37. The roller 37 is moved to the meshing position. At this time, in addition to the centrifugal force received by the roller 37 itself, the centrifugal force received by the weight body 38 is also applied to the roller 37. A weight locking portion 41 that restricts the operating range of the weight body 38 is provided on the outer diameter side of the weight operating surface 40 so that the weight body 38 cannot move further to the outer diameter side. The weight locking portion 41 is configured by narrowing the space between the cage 32 and the outer peripheral surface of the inner ring 2. Further, on the outer diameter side, a roller locking portion 42 (rolling body locking portion) for limiting the operating range of the roller 37 in the direction of the weight body 38 is provided. The weight operating surface 40, the weight locking portion 41, and the roller locking portion 42 are continuously provided in the embodiment, but are not necessarily formed continuously.

  A concave portion 31 into which a part of the weight body 38 is fitted is formed on the outer peripheral surface of the inner ring 2 facing the portion provided with the weight operating surface 40, the weight locking portion 41, and the roller locking portion 42 of the cage 32. A cam surface 47 that is a torque transmission surface of the roller 37 is formed adjacent to the recess 31, and is further on the outer diameter side of the cam surface 47, on the opposite side of the cam surface 47 from the recess 31. A non-wedge action surface 46 that is inclined more greatly than the cam surface is formed. The recess 31, the cam surface 47, and the non-wedge acting surface 46 are continuously provided in the embodiment, but are not necessarily formed continuously.

  As shown in FIG. 4, during non-rotation to low-speed rotation (range), the weight body 38 is positioned on the inner diameter side of the recess 31 and is in contact with the roller 37, and the roller 37 is pushed against the roller locking portion 42 by the accordion spring 35. It is in a hit state. Thereafter, when the inner ring 2 rotates and the rotation starts at a high speed equal to or higher than a predetermined number of rotations, the weight body 38 receiving the centrifugal force moves to the outer diameter side, and the roller 37 is moved to the meshing position of the cam surface 47. Move to. In this state, when the inner ring 2 rotates in the counterclockwise direction in the figure with respect to the outer ring 3, torque is transmitted. The state at the time of this operation is shown in FIG.

  Furthermore, when the roller 37 receives excessive torque, the roller 37 moves to the non-wedge acting surface 46 as shown in FIG. 6 so that the torque can be released. At this time, the movement of the weight body 38 toward the cam surface 47 is restricted by the weight locking portion 41. Therefore, the roller 37 moves to the accordion spring 35 side, and the contact with the weight body 38 whose movement is restricted by the weight locking portion 41 is cut off.

  Since the cage 32 of the present embodiment is mainly made of resin and the roller 37 is mainly made of metal, the friction between the cage 32 and the roller 37 compared to the case where the cage 32 is made of metal. The coefficient becomes low and the operation of the roller 37 becomes smooth. Further, the weight can be reduced. The cage 32 can be made of cast metal, aluminum, or the like.

  Next, a second embodiment of the present invention will be described with reference to FIGS. In the second embodiment, the positional relationship and operation of the weight body 38, the roller 37, and the accordion spring 35 are substantially the same as those in the first embodiment. In the second embodiment, the form of the cage is greatly different from the first and first embodiments.

  The cage used in this embodiment will be described with reference to FIGS. FIG. 12 is a development view of the first plate 60 of the cage 50 of the second embodiment, and FIG. 13 is a development view of the second plate 70 of the cage 50 of the second embodiment.

  In this embodiment, the cage 50 is formed as a first and second plate by punching a plate-shaped steel plate. FIG. 12 is a development view of the first plate 60, and the first plate 60 includes a plurality of convex portions extending from the substantially annular main body 66 in the outer diameter direction. The convex portion includes a first pillar portion 51 and a hole 62 for attaching the accordion spring 35.

  The main body 66 is further provided with a caulking hole 64 for coupling with a second plate 70 described later. Further, two engaging tongues 65 are provided in the inner diameter direction of the main body 66 in order to fix the cage 50 to the inner ring 2. It is preferable that the above-described caulking holes 64 and the engaging tongues 65 are arranged equally in the circumferential direction. The engaging tongue 65 is fitted into the concave groove 54 of the inner ring 2 and fixed to the entire inner ring 2 of the cage. That is, the concave groove 54 and the engaging tongue 65 constitute a rotation prevention mechanism that prevents relative rotation between the cage 50 and the inner ring 2.

  FIG. 13 is a development view of the first plate 70, and the second plate 70 is composed of a plurality of convex portions extending from the substantially annular main body 75 in the outer diameter direction. The convex portion includes a second column portion 72 and a caulking projection 71, and a later-described weight operation surface 52 is formed between the second column portion 72 and the projection 71.

  Two engaging tongues 74 are provided in the inner diameter direction of the main body 75 in order to fix the cage 50 to the inner ring 2. It is preferable that the convex portion and the engaging tongue portion 65 described above are arranged equally in the circumferential direction. The first plate 60 and the second plate 70 described above are bent to obtain a predetermined shape, and the two plates are coupled to each other to hold the retainer 50 of this embodiment (see FIGS. 7 and 8). Get.

  Next, details of the rotationally actuated one-way clutch 80 of the second embodiment will be described with reference to FIGS. FIG. 7 is a front view of the rotationally actuated one-way clutch 80 showing the second embodiment, and FIG. 8 is an axial sectional view of the rotationally actuated one-way clutch 80 showing the second embodiment. FIG. 9 is a diagram showing the state of the roller and the weight body during non-rotation to low-speed rotation in the second embodiment, and FIG. 10 shows the roller during operation (during engagement) of the second embodiment. FIG. 11 is a diagram showing the state of the weight body, and FIG. 11 is a diagram showing the state of the roller and the weight body at the time of eccentricity (when over torque is applied) in the second embodiment.

  In FIG. 7, the cam surface 47 and the non-wedge acting surface 46 (FIGS. 9 to 11) provided on the outer peripheral surface of the inner ring 2 are substantially the same as those in the first embodiment. The difference between the second embodiment and the first and first embodiments is that the working surface of the weight body 38 is formed on a convex portion provided on the first or second plate constituting the cage 50. It is a point.

  The caulking protrusion 71 of the second plate 70 is fitted into the caulking hole 64 of the first plate 60 and caulked to form the cage 50 by the coupling portion 53. The convex portion of the second plate 70 is bent to be located on the inner circumference of the outer ring 3, and a weight operating surface 52 having a predetermined inclination with respect to the radial direction and a weight locking portion 55 are formed. The weight locking portion 55 is configured by narrowing the space between the cage 50 and the outer peripheral surface of the inner ring 2.

  FIG. 8 is a sectional view in the axial direction of FIG. 7, and it can be seen that the cage 50 includes a first plate 60 and a second plate 70.

  Next, the operation of the rotary operation type one-way clutch 80 of the second embodiment will be described with reference to FIGS. The basic operation is the same as in the first embodiment. As shown in FIG. 9, during non-rotation to low-speed rotation (range), the weight body 38 is positioned on the inner diameter side of the recess 31, and the roller 37 is pressed in the non-engagement direction by the accordion spring 35.

  Thereafter, when the inner ring 2 rotates and the rotation starts at a high speed equal to or higher than a predetermined number of rotations, the weight body 38 that receives centrifugal force moves to the outer diameter side along the weight operation surface 52, and the roller 37 is moved. When the inner ring 2 is moved to the engagement position of the cam surface 47 and the inner ring 2 rotates in the counterclockwise direction in the drawing with respect to the outer ring 3, torque is transmitted. The state at the time of this operation is shown in FIG.

  Furthermore, when the roller 37 receives excessive torque, the roller 37 moves to the non-wedge acting surface 46 as shown in FIG. 11 so that the torque can be released. At this time, the weight body 38 is blocked by the weight locking portion 55, and movement to the cam surface 47 side is restricted. Accordingly, the roller 37 moves to the accordion spring 35 side, and contact with the weight body 38 whose movement is restricted by the weight locking portion 55 is cut off. The inner peripheral surface 3a of the outer ring 3 is displaced to the position 3b when not eccentric.

  Here, the relationship between the cage 50 and the accordion spring 35 is as follows. FIG. 14 is a schematic view of the pocket portion viewed from the outer diameter side of the second embodiment. FIG. 15 is a front view of an accordion spring mounting portion in the second embodiment.

  As shown in FIG. 14, the accordion spring 35 has a joining portion 58 that presses the roller 37 at the tip portion, and a mounting portion 57 at the root portion. The accordion spring 35 is fixed to the cage 50 by sandwiching the first column portion 51 by the attachment portion 57. Further, by engaging the tongue piece 56 formed by cutting out the attachment portion with the hole 62, the accordion spring 35 is more firmly fixed and can be prevented from falling off.

  The attachment state of the attachment portion 57 of the accordion spring 35 is shown in FIG. 15, and it can be seen that the tongue piece 56 at the tip of the attachment portion 57 is fitted in the hole 62 of the first plate 60 of the cage. According to the second embodiment, the cage 50 can be made of steel, synthetic resin, aluminum or the like. Moreover, since it can shape | mold thinly as a whole rather than the holder | retainer of 1st Example, a one-way clutch can be reduced in weight. In addition, the processing cost can be reduced.

  In each of the embodiments described above, the weight may be formed from a material such as steel, copper, a steel alloy, aluminum, or a synthetic resin. However, when a material having a large specific gravity such as steel is used, the weight is received per unit volume. Since the centrifugal force is increased, the apparatus is small in size and can be engaged even at low speed rotation, and the diameter of the weight body 38 can be reduced.

  In addition, although the cylindrical roller as a rolling element arrange | positioned at a pocket was shown, this may be a spherical body. Also, the weight may be a sphere instead of a cylindrical roller. Further, regarding the combination of the rolling element and the weight, both may be rollers, both may be spheres, one of them may be a roller, and the other may be a sphere.

  Moreover, in each Example, although the pocket is provided in multiple places in the circumferential direction, this number can be arbitrarily changed according to a required torque capacity etc., and may be other than eight places, for example, four places or six places. But it ’s okay. However, it is preferable to provide the pockets with equal distribution in the circumferential direction regardless of the number.

  In the first and second embodiments, the diameters of the roller and the weight body are substantially the same, but it is not always necessary to have the same size, but the use conditions (for example, the range of the number of rotations during operation). Can be set arbitrarily.

  The rotationally actuated one-way clutch of the present invention can be applied not only to motorcycles, snowmobiles, etc., but also to four-wheeled vehicles.

1 is a front view of a rotary actuated one-way clutch showing a first embodiment of the present invention. It is the schematic of the pocket part seen from the outer diameter side of 1st Example of this invention. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an axial sectional view of a rotary actuated one-way clutch showing a first embodiment of the present invention. It is the figure which showed the state of the roller and weight body at the time of non-rotation-low speed rotation in 1st Example of this invention. It is the figure which showed the state of the roller and weight body at the time of the action | operation (at the time of engagement) of 1st Example of this invention. It is the figure which showed the state of the roller and weight body at the time of eccentricity (when overtorque is received) of 1st Example of this invention. It is a front view of the rotation actuated one-way clutch showing a second embodiment of the present invention. It is an axial sectional view of a rotary actuated one-way clutch showing a second embodiment of the present invention. It is the figure which showed the state of the roller and weight body at the time of non-rotation-low speed rotation in 2nd Example of this invention. It is the figure which showed the state of the roller and weight body at the time of the action | operation (at the time of engagement) of 2nd Example of this invention. It is the figure which showed the state of the roller and weight body at the time of eccentricity (when overtorque is received) of 2nd Example of this invention. It is an expanded view of the holder | retainer (1st plate) of 2nd Example of this invention. It is an expanded view of the holder | retainer (2nd plate) of 2nd Example of this invention. It is the schematic of the pocket part seen from the outer diameter side of 2nd Example of this invention. It is a front view of the accordion spring attachment part in 2nd Example of this invention.

Explanation of symbols

30, 80 Rotation actuated one-way clutch 2 Inner ring 3 Outer ring 35 Accordion spring 37 Rolling element (roller)
38 weight 40 weight working surface 47 cam surface

Claims (8)

An outer ring having an inner peripheral cylindrical surface, an inner ring formed with a cam surface, a rolling element that transmits torque between the outer and inner rings, a biasing spring that biases the rolling element, and a biasing force that receives centrifugal force In the rotationally actuated one-way clutch provided with a weight that presses the rolling element in the engaging direction while resisting the biasing force of the spring,
A cage for holding the weight body is provided, and the cage is provided with a weight operating surface for guiding the weight body and an outer diameter side of the weight operating surface, and the weight body moves in an outer diameter direction. A rotary actuating one-way clutch, characterized by being provided with a weight locking portion for limiting the weight . 2. The rotationally actuated one-way clutch according to claim 1, wherein the retainer further includes a bearing portion that holds one of the rolling elements and the biasing spring and supports the outer and inner rings. .   A plurality of window portions for positioning at least one of the rolling element, the weight body, and the biasing spring are formed in the cage, and the bearing portion is provided between the window portions. The rotation actuated one-way clutch according to claim 2, wherein the one-way clutch is provided. The rotation actuated one-way clutch according to any one of claims 1 to 3, further comprising a rotation prevention mechanism that prevents relative rotation between the retainer and the inner ring . The rotation actuated one-way clutch according to any one of claims 1 to 4, wherein the retainer is made of resin . Formed by the outer peripheral surface of the inner ring and the window portion of said retainer, said weight body, according to claim 3, characterized in that the rolling element or at least one is receiving pocket of the biasing spring is provided The rotary actuated one-way clutch described in 1. A concave groove extending in the axial direction is provided on the outer periphery of the inner ring, while a convex portion is formed at a position corresponding to the concave groove on the inner periphery of the cage, and the convex portion is fitted in the concave portion. The rotationally actuated one-way clutch according to any one of claims 1 to 6 , wherein the retainer is attached to the inner ring by matching. The rotationally actuated one-way clutch according to any one of claims 1 to 7, wherein a communication portion that allows the weight body to be visually recognized from the outside during non-rotation is provided in the inner ring .

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